Mining machine



Feb. 1, 1944. R. K. JEFFREY ETAL MINING MACHINE Original Filed Max 6, 1938- 5 Sheets-Sheet 1 /NVEN TORS ROBE T K. JEFFREY, '4

AND LEWIS E. MITCHELL,DECEA5E RICHARD D. NICHOLS, Avmmzsmmolg Feb. 1, 1944.

R. K. JEFFREY ETAL 2,340,533

MINING MACHINE Original Filed May 6, 1938 s sheets-sheet 2 L9 {5- .//w5/97-o1es- ROBERT K. JEFFREY,

AND EMrrcHELLDEcmu; v j DNIcHoL's, Anmmsmmn Feb. 1, 1944. R. K. JEFFREY ET AL MINING MACHINE Original Filed May 6, 1938 5 Sheets-Sheet 3 /NVE/Y7'OlS ROBERT K. JEFF'IQEX AND LEWIS E. MITCHELL, DECEASED, RICHARD D. Nucuous, ADMINISTRATOR BY 6X44 ATT'Y 1,1944. R. K. JE FREY Em 2 3 5 MINING MACHINE Original Filed May 6, 193a 5 Sheets-Sheet 4' /Nl/EN 7095 I Real-RT KJEFFREX AND Levws E. MITCHELL, DECEASED; RICHARD D. NICHOLS, Apmmsmmog Feb. 1, 1944. R. K.'JEFFREY ETAL MINING MACHINE Original Filed May 6, 1938 5 Sheets-Sheet 5 Hosea-r K. JEFFREY,

AND Lawns E.MITCHELL,DEC

Q snwog RICHARD D. N|cHoLs,AbMm| BY k;

Patented Feb. 1, 1944 UNITED STATES PATENT OFFICE MINING MACHINE Robert K. Jefi'rey, Columbus, Ohio, and Lewis E. Mitchell, deceased, late of Columbus, Ohio, by Richard D. Nichols, administrator, Columbus, Ohio, assignors to The Jeffrey Manufacturing Company, a corporation of Ohio Original application May 6, 1938, Serial No.

206,448. Divided and this application November 4, 1940, SerialNo. 364,324

11 Claims.

This invention relates to a mining machine and particularly to mechanism for propelling a min ing machine during transportation.

An object of the invention is to provide a mining machine which can be fed at a sumping speed, which speed may be varied continuously and progressively in accordance with the hardness of the material being cut.

A further object Of the invention is to provide feeding means for a mining mechanism, such as a kerf cutter, includin hydraulic feed mecha- A further object of the invention is to provide improved mechanism for driving a mining machine or other vehicle at avariety of speeds.

Still another object of the invention is to provide an improved hydraulic system for adjusting certain adjustable devices of a mining machine.

Other objects of the invention will appear hereinafter, the novel features and combinations being set forth in the appended claims.

This application is a division of our application Serial No. 206,443 filed May 6, 1938, for an improvement in Mining machines, which matured into Patent No. 2,263,779; November 25, 1941'. I

In the accompanying drawings:

Fig. 1 is a diagrammatic plan view showing a mining machine incorporating the structure of our invention;

Fig. -2 is a plan view of the rear end of the mining machine shown in Fig. 1;

Fig. 3 is a plan view of the truck of the mining machine showing parts in section;

Fig. 4 is a transverse sectional view taken on the. line 4-4 of Fig. 2 looking in the direction of the arrows;

'Fig. 5 is a transverse sectional view taken on the line 5-5 of Fig. 2 looking in the direction of the arrows;

Fig. 6 is a longitudinal sectional view showing the, drive for the truck and taken on theline 5 of Fig. 5 looking in the direction of the arrows;

Fig. 7 is a diagrammatic illustration of the hydraulic'control system of a portion of the mining machine which is the subject matter of the invention herein claimed; and

Fig. 8 is a sectional elevational view of a volume control and pressure relief valve employed in the system of our invention.

In Fig. 1 of the drawings there is illustrated diagrammatically a mining machine which incorporates the features of the invention herein claimed. The mining machine is disclosedin full detail in our parent application above identified, of which this application is a division, and.

i so no attempt will be made to describe it in detail in its entirety, only those parts forming the subject matter of the invention herein claimed being specifically described.

,Said mining machine includes a truck which supports a turntable 1| upon which is mounted for adjustment in a vertical plane asupplementary frame, I which has a forwardly extending neck I09 carrying a turnover head mechanism 59 which provides for various adjustments of kerf cutting mechanism I60.

Extendingrearwardly from and supported by the truck 45 is a platform 545 which carries a considerable amount of mechanism some of which per se is not pertinent to the invention herein claimed.

The truck 45, best seen in Fig. 3 of the drawings, comprises a main frame formed by spaced apart longitudinally extending frame members 45, 46 whichare-laterallyspaced apart and between which extend transversely extending forward platei ll and transversely extending rearward plate 48 and intermediate transversely extending bolster members 49 and 55. All of said mainframe members 46 to 58], inclusive, are rigidly attached together to form, a strong main frame for the truck 45. Said main frame is supported upon a forward axle 5| and a rearward axle 52, which axle 5| is slidably journaled in adjustable journal boxes 53, 53 which may be longitudinally adjusted by adjusting screws 54, 54 to adjust the tension of thedriving chain. To assure movement of the axle 5| in parallelism the adjusting screws 54, 54 are connected to rotate together by chain and sprocket mechanism 55.

The journal boxes 53, 53am held in the main frame against longitudinal movement but provide for limited vertical movement thereby to permit the shaft 5| to move relative to the longitudinal axis of the truck .45 to provide a modified three point suspension for said-truck 45 so it may readily accommodate itself to the unevenness of 'spectively. I

As clearly illustrated in Fig. 7 of the drawings,

the mine tracks over which the mining machine travels.

The rear end axle 52 is rigidly journaled to the main frame of the truck 45 by appropriate journal bearings 56, 56. The axles 5! and 52 are provided with appropriate driving and supporting track engaging flanged wheels 5'! all of which are keyed to the respective axles 5! and 52 by keys 58. The axles 5!, 52 are connected to rotate in unison by chain and sprocket mechanism 59. It is thus evident that any driving force supplied to axle 52, as hereinafter described, will be transmitted to all four of the wheels 5! thereby insuring a maximum of traction for propelling the mining machine which is particularly desirable during sumping operations. It is,'of course, evifor swinging the turntable 1!. Said hydraulic system includes a supply tank 389 for the hydraulic fluid, preferably oil, from which extends a feed pipe 38! associated with a filter 382 in the bottom of said supply tank 389. The feed pipe 38! leads to a pressure control valve 383.

Said pressure control valve 333 comprises a block provided with check valves 336 and 38'! leaddent that the afore-described adjusting screws 54' provide for the tensioning of the chain and sprocket mechanism 59 by the forward and rearward adjustment of the axle 5!.

I It is of course evident that the flanged wheels 5'! are adapted to ride upon rails in a mine either for transporting the mining machine from one place to another or for supporting said mining machine while performing a mining operation. While we prefer this track mounted type of truck said truck may be mounted in any other desired manner as upon endless treads to operate in a trackless mine room.

In addition to those elements above described the truck 45 also includes a top plate 19 which is rigidly attached to the frame members 43, 4! and 48.

Mounted upon the truck 45 fo'r'swinging movement in a horizontal plane or about an upright axis is a turntable H. (Fig. 1.) The turntable I! has attached at its center a casting or pedestal I5. (Fig. 3.) r v 'To provide'for the swingingmovernent of the turntable 1! about its upright axis with respect to the truck 45, the lower portion of the casting 15 is provided with a pair of spaced integral gears 19 with which cooperate a pair of racks 89 and 8! having spaced top and bottom teeth.

To apply turning movement to said turntable I! through the racks 89 and 8! they are con.- nected to hydraulic'piston motors 82 and 83, re

a pipe 95 leads to the head end of thepiston motor 83 and a pipe 96 leads to the piston rod end thereof. Similarly associated with the motor 92 is a pipe 9'! leading to the head end and a pipe 98 leading to the piston rod end.

As disclosed completely in said parent application, the two hydraulic piston motors B2 and 83 are always operated together and in reverse directions so that a verypowerful and equalizing -force will be'transmitted to the turntable I! to swing it.

As best seen in Fig. 1 of the drawings, there is mounted upon the turntable H for movement about a horizontal axis a supplementary frame l99 formed by a rigid motor'casing !9! within which is housed an electric motor for driving the kerf cutting mechanism I69 to the forward end of which is attached a gear casing having a downwardly sloping neck I99.

Attention is now directed particularly to Fig. '7 of the drawings which illustrates diagrammatically a portion of the hydraulic control system for operating the mining machine including particularly apparatus carried by platform 545 and the control for hydraulic piston motors 82 and 83 ing to chambers 388 and 389, respectively. Communicating with the chambers 388 and 389 are pipes 399 and 39!, respectively, which form the feed pipe'andi out-put pipe, respectively, of a high pressure pump 392 which, for example, may be of the gear type and capable of producing a pressure of aproximately 1500 pounds per square inch. The pressure control valve 383 also includes ballcheck valves 393 and 394 which com- ,municate with chambers 399 and 389, respectively. Associated with the ball check valves 393 and 394 is pressure pipe 399 which is the main pressure pipe for the hydraulic system.

The function of the pressure control valve 393 is to insure that the pipe 38! will act as a feed pipe and that it will be under suction at all times and the pipe 399 will act as a pressure pipe and be under pressure at all times, regardless of the direction of rotation of the gear pump 392; For example, if the gear pump 392 is operated in its normal direction to draw in oil through pipe 399 and discharge oil through pipe 39!, check valve 386 will be open to provide communication between pipe 38! and pipe 399 and due to the pressure in pipe 39! check valve 38'! will bemaintained closed. At the same time, due to the pressure in chamber 3339 check valve 394 willbe open to supply oil under pressure to pressure pipe 399 and check valve 393 will be held closed by the pressure to said pipe 399. 7

Should the pump 392 reverse its direction of rotation and draw in oil from pipe 39! and deliver oil under pressure to pipe 399, check valve 38! will open to supply oil from pipe 38! to said pipe 39! and check valve 386 Will'be held closed by the pressure in chamber 389. Also check valve 393 will be open due to the pressure in chamber 388 to provide communication between pipe 399 and pressure pipe 399. Furthermore, due to the pressure to said pipe 399 check valve 394 will be maintained closed. It is thus evident that pressure pipe 399 will always be the main pressure lines of the hydraulic system'and that pipe 38'! will always be the main feed line of the hydraulic system without regard to the tion of pump 392.

The pressure pipe 399 leads to a volume control and pressure reliefvalve 499 which, as its name indicates, acts to control the volume of fluid direction of rota delivered to the hydraulic system by the pump and within which is a rotary control cylinder 493 having a removed portion 494 and carried on a shaft 495 with which is associated an operating lever 496 to adjust the position of the control cylinder 493 in the chamber 492. By adjusting the cylinder 493 the size of the opening afiorded between inlet port 491 and outlet port 498 of the chamber 492 may be regulated thereby controlling the volume of fluid which flows from the p e pip 99 to thepressurepipe 40.9.. leading from the volume control and-pressurerelief valve 400 which pressure pipe 409 isincommunie cation with the outlet'port 408,; It is thus evident that the operating lever 406 may be adjusted to control the normal volume of hydraulic fluidto be supplied to the pressure pipe 409.

Associated with the pressure pipe 409 is a pipe 410 which leads to a pressure gauge 4| I which will, of course, indicate the pressure in the pressure pipe 409 at all times.

To provide for the high pressure relief feature of the valve 400 the block 4!" is provided with a cylindrical chamber 4 l 2 the bottom ofwhich is in communication with the inlet port 40! and above which port 401 is a circumferential chamber-M3. Within the chamber M2 is a piston 4-l4 urged to bottom seating position by a coil spring M5, the top of which rests againsta plug 416 threaded in the top of block 40!. A connecting pipe 4|! leads from the pipe 4H1 to a bore 4l8 of restricted size which communicates with the chamber 412 at a position above the piston 4l4.

Also communicating with the chamber M2: at a position above piston M4 is a larger bore 4I9 leading to a chamber 420 whichis connectedby a.

vertical bore 42| to a drainpipe 422 which also communicates by a bore 423, with the chamber 413. Within the chamber 420 is a ball relief valve 424 provided with a compression spring 425, the compression of which may be adjusted by adjusting screw 426.

In normal operation the piston 4l4 automatically assumes a floating position in chamber M2 to by-pass just enough hydraulic fluid to maintain a fluid flow from; pipe 399-to pipe 409 through the adjustable orifice, provided by removed: portion 404, to maintain said piston 4l4 in a condition of equilibrium, whereby it will operatetobypass an amount of hydraulic fluid as determined by the adjustable position of handle 406 to insure,

delivery of a variable predetermined amount of hydraulic fluid at all times, under the control of the operator, to the saidpipe 409, the remaining portion of the hydraulic fluid delivered by thepump 392 to the pipe 399 being by-passed byway of port 401, chamber M3 and bore 423 to drain pipe 422. The delivery rate to pipe 409 is therefore determined solelyby the position of handle 406.

The adjustable pressure drop across the adjustable orifice provided by removed portion 404 is of course the controlling factor in maintaining this condition of equilibrium because this pressure drop is supplied to the floating piston 414. Any decrease in fluid flow to pipe 409 from that required by the setting of handle 406 will causethe piston M4 to move downwardly thereby reducing the amount of liquid by-pass from pipe 399 to drain pipe 422 which will immediately correct this condition. Conversely, any increase in fluid flow to pipe 409 from that required by the setting of arm 406- will cause the piston 414 to move upwardly thereby increasing the amount of liquid by-passed from pipe 399 to drain pipe 422 which will correct this condition.

The valve 490 has a, high pressure relief function by virtue of ball relief valve 424. For example, should the pressure in the pipe 409 exceed 12,000 pounds per square inch, or any other amount depending upon the setting of ball relief valve 424, said relief valve 424 will open to per- Init fluid under pressure in'the chamber 4I2 to flow through bores M9 and 42 l to drain pipe 422.

The. opening of valve 424 may be due to a radual, increase in pressure. communicated through bore 4) or to a sudden increase which will move piston 4M upwardly since the pressure aboveit will not be equalized immediately due to the drop through said bore 448.

When ball valve 424 opens, reduced pressure is provided above piston M4. The higher pressure below piston 4l4 then lifts it. As a consequence of any of the above conditions the piston 4l4 will be lifted above its normal position to permit more or all of the fluid under pressure in port 40'! to how to the chamber M3 and thence to drain pipe 422 by way: of bore 423.

It is evident that after a high pressure condition is relieved, the relief valve 424 will operate to close the bore 4 i 9 thereby to restore said piston 4M toits normal condition.

As a safety feature we also provide a by-pass around the relief valve 424 which may be manually operated in case said relief valve becomes inoperative for any purpose. This by-pass is formed by a pipe 42'! communicating with bore 9 and extending to manually operated relief pilotvalve 428, the structure of which is disclosed in full de tail in our parent application above identified.

Thus should any emergency arise in which the automatic pressure relief function of the valve m is not performed, it may be relieved by the manual operation of the relief pilot valve 428 which interconnects pipes 421 to a drain pipe 440 leading to drain pipe junction box 44!.

It may also be noted at this point, by reference to Fig. 7 of the drawings, that a drain pipe 442 extends between the pump 392 and the junction box 44! to provide for the return of any oil which doesnot flow in the proper path, particularly such oil as leaks pastbearings or bushings.

From that portion of the hydraulic control system abov described it is manifest that hydraulic fluid under regulated pressure and volume is supplied to the pressure pipe 490 which, as clearly illustrated in Fig. 7 of the drawings, leads, to a two unit control valve 443 which has two manually operable control pistons. It may be stated that the two unit control valve 443 has one slide piston 520 (Fig. 4) which is operative to control the hydraulic piston motors 82 and. 83 for swinging the turntable H about its upright axis; and another slide piston 5H1 which is operative to control a rotary type of hydraulic, motor 444. to effect slow speed or sumping travel of the mining machine, as hereinafter described in complete detail.

It may also be stated that excess fluid drain pipes 445 and 446 are provided for the control valvev 443 and hydraulic motor 444, respectively, which lead to the junction box 44! and, in turn, to the drain pipe 422.

It may also be stated that without regard to the positions of the slide pistons H9, 520 of the two unit control valve 443, pressure will always be available to a flexible rubber hose pressure pipe 44? which extends therefrom and leads to further hydraulic control valves disclosed completely in our parent case which per se are not pertinent to the invention herein claimed. Slide piston 5l9 controls the flow of hydraulic fluid under pressure from pressure pipe 409 by way of pipe 522 or 523 to rotary sumping hydraulic motor 444 for driving the mining machine at a slow sumping or kerf cutting speed, as hereinafter described, and slide piston 525 controls the flow of fluid under pressure from pressure pipe M39 from the afore-described control unit 400 by way of pipe 524 01'525 to the hydraulic piston motors 82 and 83 which are reversely connected in parallel to swing the turntable 1|, It is to be understood that reverse operations of the .two mentioned slide pistons l9 and 526 will produce a reverse operation of the motor 464 in the one instance and of the motors 82 and 83 in the other instance. It is also to be understood that when in their normal positions the slide pistons 516 and 526 will lock the motor 444 and the motors 82, and 83, respectively, in their adjusted positions and provide a no-load by-pass for pump 392.

As clearly seen by reference to Figs. 2 and 4 of the drawings, in the corner provided by the side plate 561 and the supplementary rearward plate 55l of the platform 545, the hydraulic fluid supply tank 386 is supported. Adjacent the opposite forward corner of the platform 565 and supported upon the supplementary rearward plate 55i is the two unit control valve 543. The volume control and pressure relief valve 465 and the relief pilot valve 628 are likewise carried on the supplementary rearward plate 55i near the two unit control valve 443. The pressure gauge ll I is supported by the supplementary side plate 556 which is provided with a window 552 (see Fig. 4) so that said gauge may be easily read.

It is to be noted by reference to Figs. 2 and 4 that a pair of operating means 556 and 5514 are associated with the slide pistons 519 and 526, re-

' spectively, of the two unit control valve 463 each of which comprises a pivoted lever pivoted to a bracket 555 and extending respectively through slots 556 and 551 in the plate 55l whereby they will be readily accessible at a position adjacent the turntable H where other controls are located.

rest of said hydraulic system which is not illus-' trated being carried by the supplementary frame 166. It is for this purpose that the pressure pipe 461 and the drain pipe 558 are both made of rubber hose since there is, of course, appreciable movement'of the supplementary frame I65 both about a horizontal axis and a vertical axis with respect to the platform 545. It is to be noted, however, that only these two hoses extend between these relatively movable parts.

Referring again to Fig. 4 of the drawings, it is to be noted that at their right hand ends each of the slide pistons 5l9 and 526 is provided with automatic spring controlled centering mechanisms 559and 566, respectively, which operate automatically to center said slide pistons 5H6 and 520 whenever they are released.

Referring now particularly to Figs. 2 and 4 it is seen that supported from a bottom plate 546 of the platform 545 is an electric motor 55! with which is associated control mechanisms in ccntrol box 562 and starting resistors in resistor box 563. The electric motor 56! is for driving the mining machine both at transportation and sumping speeds through the mine and for oper ating the oil pump 592 to provide hydraulic fluid, such as oil, under pressure to the previously described hydraulic control system. The electric motor 56! drives gear mechanism supported upon platform 564 (see Fig. '4) supported from the bottom plate 546 and comprising a pinion 565 (Fig. 2) keyed to the armature shaft of said elec. tric motor 56!. Pinion 565 meshes with two gears 566 and 561, the latter'of which is keyed to a counter-shaft 568 (Fig. 4) which is journaled in housing 565 by spaced ball bearings 516 and 51!. Surrounding the counter-shaft 568 and mounted for free rotation with respect thereto is a sleeve 512 mounted in housing 569 upon ball bearings 513 and 514. Keyed to said sleeve 512 is a worm gear 515 meshing with a worm 516 which is driven through gear reduction mechanism 511 from the rotary type bydraulic motor 444 (Fig. 2), previously described.

It will be noted by reference to Fig. 2 of the drawings that the gear housing 569 and the housing of gear reduction mechanism 511 are rigidly connected together and are rigidly connected to the housing of rotary hydraulic motor 446 wherebythey will all be supported from the platform 564.

Also surrounding the counter-shaft 568 is a sleeve 518 mounted on said shaft 568 by roller bearings 519 and 580. Intermediate its ends the counter-shaft 568 is providedwith a plurality of dogs or jaws 58L for the purpose of effecting a driving relation with the sleeve 518 by way of cooperating jaws 582 formed on slide sleeve 583 which is feathered to the outer portion of sleeve 516 by cooperating key-ways and keys 584. The jaws 582 are also adapted to cooperate selectively with jaws 565 on sleeve 512 to efieot a driving relation between sleeves 512 and 518. It is evident that in the central position of the jaws 562, as illustrated in Fig. 4 of the drawings, neither the sleeves 512 and 518 nor the shaft 566 and the sleeve 518 are connected together. This, of course, represents a neutral position.

Operating means for the sleeve 563takes the form of a shipper 586 operable by a pivoted bell crank 561 (see Fig. 2), pivoted to a bracket 568 and operable from a rod 565 which, in turn, is

" operated from rod 598 through-pivoted bell crank journals in bracket 594 and operable .by handle 595 which is adjacent operator's seat 596 at the rear left-hand corner of the platform 545. It is thus evident that by controlling the handle 535 a driving connection may be made to the sleeve 5'58 from the electric motor 56! through the gears 565 and 561, the shaft 568 and jaws 58! and 582, or from the rotary hydraulic motor 456 through the gear. reduction mechanism 511, worm 516 and worm gear 515, sleeve 512 and jaws 582 and 585. The former drive is employed as a high speed drive'for the mining machine. for transportation purposes and the'la'tter drive is employed for a low speed or sumping drive when the mining machine is cutting a kerf.

It may be stated that in normal operation, the jaws 532 will engage either jaws 5a! or 565 so that either a high'speed or a low speed connection will be effected at this point. To maintain either of the mentioned driving relations the bell crank lever 581 has associated with it spring compression mechanism 591 operative to urge the slide sleeve 583 either to the right or to the left as the arm of the bell crank lever 581 passes to either side of the vertical alignment with spring compression mechanism 591, as will be evident from reference to Fig. 2 of the drawings. This spring compression mechanism will not only maintain the jaws in locked relation but will aid their movement into interlocking relation under the controlling influence of operating handle 595.

"aardes's A'djacentits outer endthe sleeve 518 isprovided with an integral gear 598 which'm'eshes with a large gear 599 (see Figs. 2 and5), provided with alarge hub 666 having spiral jaws GUI and keyed to a second counter-shaft 662 journaled in bearings663 and 664 carried by upright plates 665 and 666, respectively, the former of which is supported from bottomplate 546 and'the latter of which is supported from platform 564.

Loosely journaled on the counter-shaft 662 is a"drive sprocket 661 provided with jaws 666 adapted to be engaged with and disengaged from jaws 669 of clutchsleeve 616 keyed to and slidable on counter-shaft 662 by a pivoted shipper 6llpivoted on'shaft 6l2 andoperable by 'rod 6l3 (see Fig. 2) which maybe adjusted longitudinally of itself byhandle 6l4 which may be placed on either side of stop lug 615 carried on the top of control box 562. It will be evident that by moving handle 614 to one side of stop lug 6|5 the jaws 668 and 669 will be engaged and by moving it to the other side they will become disengaged. It is by virtue of this clutch that the operating or non-operating connection is made for driving the mining machine either at a sumping or transportation speed.

Below the drive sprocket 661 is a pair of guide and tensioning sprockets N6 and 6|! (Figs. 5 and 6) mounted on shafts 6l8 and H9, respectively, both 'of which are carried by a pivoted chain adjustingarm 626 pivotally mounted by pin 62l on a pair of upright plate 622 and 623 supported from bottom plate 546, the free end of which arm 626 has cooperating therewith a chain adjusting set screw 624 which may be adjusted to swing said arm 626 about the axis of pin 62!. I

Reeved about the sprockets 661, 6l6 and 6|! and about a sprocket 625, keyed to the rearward axle 52 -of the, truck 45, is a drive chain 626, the lower run of which is supported intermediate the sprockets H6 and 625 by a bearing pad62'l and the upper run of which is supported intermediate the sprockets 6H and 625 by bearing.

pad 626. It is evident that by swinging the arm 626 about the pin 621 under the influence of the set screw 624 the tension of drive chain 626 may be adjusted. It is to be particularly noted that the drive chain does not extend in a straight line between the sprocket 661 and the sprocket 625 but is generally L-shaped. This provides for a relatively large amount of adjustment in the length of the chain 626 so that the distance between the axle 52 and the shaft 662 need not be determined with extreme accuracy. It all provides for a relatively large take-up which may be caused by stretching of the chain 626 so that a complete link of the chain 626 may be removed without extending beyond the limits of adjustment thereof afforded by the arm 626.

Also associated with the previously described hub 666 of the gear 599 and featheredto the outside thereof is a clutch sleeve 636 having spiral jaws 63l adapted to be selectively placed in engagement with or disengagement from the jaws 66I of said hub 666 to effect a driving connection between said hub 666 and a chain sprocket 632 and for driving an electric cable reel mech-j anism 659. Shifting movement of the clutch 636 iseffected by a pivoted spring pressed shipper 633 holding jaws GUI and 63l normally engaged and pivoted to shaft 634 'andoperableby'rod 63.5 and crank 636 carried at the end of shaft 631 appropriately journaled in bracket 594 and having an operating handle 638 associated therecarries ,a steel cable. 644 which is particularly usefulin case theminin'g machine is operated in very hard coal in which case it is employed to supplement the drive effected by wheels 5] or, in 'case'the mining operationis being carried on up a slope. The cable 644 isadapte'd to be reeved about guide pulleys 645 or 646 at opposite sides of the platform 545 which are preferably journaled on pivoted brackets 64'! and 648, respectively.

Itwill be noted by'reference to Fig. 5 of the drawings, that the gear 639 is feathered on the end of shaft 662 forsliding movement along the axis thereof to be brought into mesh with gear 646 or brought out of mesh therewith. To effect this sliding movement of gear 639 We provide a shipper '64.! adapted to slide upon rod 656 provided withretaining notches 651 and 652 with which a spring pressed detent 653 is adapted to be selectivelyinserted. An operating handle 654 is provided fortlie, detent 653. It will be evident that when detent 653 is in notch 65l there will be a driving relation between gears 639 and gears 646 and when detent 653 is in notch 652 this driving relation will no longer exist.

Itis furthermore to be noted by reference to Fig. 5 of the drawings, that the gear 566 which is driven from pinion 565 (Fig. 2) has an integral shaft 655 mounted in anti-friction bearings 656 in upright plate 666and is keyed to a drive shaft 65! of the hydraulic pump 392 of the previously described hydraulic control system. It is thus to be noted that whenever the electric motor '56l is in operation the hydraulic pump 392 Will be in operation to supply hydraulic fluid, such as oil under pressure, to the hydraulic control system. It is furthermore to be noted, that this is entirely independent of the operation of the electric motor. on supplementary frame I66 which drives the kerf cutting mechanisml66. In other wordsythe drive for moving the mining machine along the mine track is ntirely independent of the drive of the kerf cutting mechanism.

As Was previously pointed out, rotation of the turntable ll about an upright axis with respect to the truck 45 is eifected by the piston motors 82 and 83 which are controlled by the two unit control valve 443 and particularly by slide piston 526 thereof controlled by anoperating means 554 (Fig. 4) which is adjacent the forward lefthand end of platform 545 and close at hand to the operating station. I

It is also desirable to be able to control said hydraulic motors to swing the turntabl H from the operators seat 596 astlie' mining machine is transported along the, minetracks through the mine, particularly to adjust the supplemental frame I66 and the kerf cutting mechanism I66 to round curvesin the mine. Therefore, vv'e'provide at the opposite end of slide valve 526 a pivoted operating bell crank "H6 (see Figs. 2 and 5) operable by. rodll] whichis controlled by handle 1J8 positioned nearthe handles595 and 638, all of whichare readilyoperable by an operatoron seat 596, w ere .the operator will "ride when the mining machine is being transported through the mine. It may additionally .be pointed out that control handles H6 and 120 areprovided within reach of the operator on seat 506 for controlling the motors 56l and the motor on supplementary frame I00.

In the-operation of the mining machine it may be pointed out that the motor 56! is the primary source of power for effecting all adjustments, including all feeding of the machine both while tramming and while sumping. The kerf cutting mechanism I60, however, alone is not driven from thesmotor 56! but is driven by a separate motor carried on supplementary frame I as fully disclosed in complete detai1 in our parent application above identified.

From a broad description it is evident that to efiect a tramming speed of movement of the mining machine by which it is of course transported from one position in the mine to another position, there is a direct connection between the reversible electric motor and the traction wheels 51 or endless traction treads, in case they are substituted for wheels 51. During this type of operation the drive is from pinion 565 of motor 56l through gear 561, shaft 568, jaw 58l and. 582 which are in operative relation, sleeve 518 intermeshing gears 598 and 599, shaft 602, engage jaws 608 and 609, sprocket 601, chain 626, sprocket 625 and rear shaft 52 which, as

previously described, is keyed to'rear wheels 51 of the truck 45. Shaft 52 as above described is also connected to drive front shaft 5| through chain and sprocket drive mechanism 59 whereby all four wheels of the truck ar driven. This gear train is of course entirely mechanical and it may be noted that it involves two clutches, one having jaws 58!, 582 (Fig. 4) the other having jaws 608, 609. Jaws 58l and 582 are normally engaged. Jaws 608 and 609 are normally disengaged. Before th motor -56l is started by way of its electrical contactors and resistors, jaws 608 and 609 are engaged when a high speed or tramming speed of transportation is desired. In case jaws 603 and 609 are disengaged it is impossible to operate the mining machine by means of traction wheels 51 and these jaws are disengaged whenever'the machine is positioned ad- J'acent a mine face to perform a mining operation. It is possible to feed the miningmachine even with the jaws 608, 609 disengaged by means of the steel cable 644'fin a manner which is obvious from the above description, and this cable 644 may be used either aloneor with the traction wheels 51 to effectsumping feeding of the machine.

' To effect a sumping feeding operation through track wheels 51 or any other traction devices which may be substituted for them the driving connection from motor '56! is through pinion 565, gear 566, pump 392 which provides hydraulic fiuid under pressure over the system disclosed inFig. '1 by which motor 444 is driven under the control of the operator and by way of slide piston m of control valve 443. The hydraulic pump 392 and hydraulic'motor 444 when operatively connected therefore constitute a hydraulic linkage in this drive system or gear train. The gear train continues from hydraulic motor 444 through gear reduction mechanism 511, worm 516, worm gear 515, jaws 585 and 582 which are engaged to efiect this driving operation by shifting of the latter jaws as above described.

The gear train then continues from jaws: 582 over exactly the same path previously traced for the complete mechanical coupling which. was

effected for high speed or tramming operation.

Of considerable importance is the fact that the speed ratio between the electric motor 56] and thetraction wheels 51 may be varied in a continuous manner by virtue of the hydraulic link effected by pump 392 and hydraulic motor 444 and the control mechanism so that'the sumping speed may be adjusted'in a continuous manner over a relatively wide range between-the maximum sumping speed possible and substantially zero sumping speed. This speed adjustment is effected by the simple expedient of adjusting handle 406 of the volume control mechanism 400. As this adjustment provides a variable orifice or opening which is continuous in its variation, that is, it isnot a step by step adjustment, the speed variation possible is a smooth continuious curve. This speed variation is of course effected by virtue of the fact that the volumelof liquid delivered to the motor 444 from the pump 392 is automatically adjusted by adjusting the handle 406 of volume control mechanism 400 and of course the speed of rotation of hydraulic motor 444 is determined by the volume of hydraulic fluid which is delivered to it per unit of time.

It is also to be noted that this variable rate of operation is not confined to the motor 444 but also extends to the piston motors 82 and 83 which swing the turntable 1| and consequently the swing feed rate of the kerf cutting mechanism I60 may be variably adjusted between wide limits in exactly the same manner that the feed rate of the kerf cutting'mechanism I60 is ad.- justed by adjusting the sumping feed rate of the entire mining machine.

' It is thus evident that a very flexible drive mechanism has been provided and one which provides for a highly desirable adjustable feed rate forthe mining machine and for the kerf cutting mechanism, both during rectilinear feeding of said kerf cutting mechanism and during swinging feeding thereof.

Obviously those skilled in the art may make various changes in the details and arrangement of parts without departing from the spirit and. scope of the invention as defined by the claims hereto appended, and we therefore wish not to be restricted to the precise construction herein disclosed.

Having thus described and shown an embodiment of our invention, what we desire to secure byLetters'Patent of the United States is:

I 1. In a mining machine, the combination with 1 a supporting frame, of propelling mechanism therefor comprising a countershaft, a driven element mounted for free rotation on the axisof; the countershaft, a drive element also mounted;-

for free rotation on theaxis of said countershaft; a motor connected to said countershaft to drive the same, another motor connected to saidd-rive element to drive the same, and clutch mechanism for selectively connecting said counter shaft or said drive element to said driven elee ment and thereby secure operation ofthe pro;

pelling mechanism from either of said motors; 2. In a mining machine, the combination with supporting framework, of mining mechanism mounted thereon, means for driving said mining mechanism, fluid-pressure operated mechanism for feeding said mining mechanism bypropelling the entire mining machine including a control valve, and means for regulating the rate of feed at any predetermined maintained value between the maximum rate and zero by controlling the volumetric flow of the fluid-pressure medium when said control valve is fully open.

3. In a mining machine, the combination with a main frame, of a kerf cutter thereon traction means for propelling said mining machine, mechanism for driving said traction means comprising a primary driving motor, a high speed drive comprising a disconnectable mechanical gear train interconnecting said motor and said traction means, a low speed drive comprising a disconnectable gear train interconnecting said motor and said traction means including a hydraulic pump driven by said primary driving motor, a hydraulic motor, drive gearing connecting said hydraulic motor to said traction means, and control means for said hydraulic motor including mechanism to vary the rate of hydraulic fluid delivery from said pump to said hydraulic motor by controlling a by-pass for said pump.

4. In a mining machine, the combination with a main frame, of a kerf cutter thereon, traction means for propelling said mining machine,'mechanism for driving said traction means comprising a primary driving motor, a disconnectable gear train interconnecting said motor. and said traction means including a hydraulic pump driven by said primary driving motor, a hydraulic motor, drive gearing for connecting said hydraulic motor to said traction means, and control means for a said hydraulic motor including mechanism to vary the rate of hydraulic fluid delivery from said pump to said hydraulic motor by controlling a by-pass for said pump.

5. In a mining machine, the combination with a main frame, of a kerf cutter thereon, traction means for propelling said mining machine, mechanism for driving said traction means comprising a primary driving motor, a disconnectable gear train interconnecting said motor, and said traction means including a hydraulic pump driven by said primary driving motor, a hydraulic motor, drive gearing connecting said hydraulic motor to said traction means, and control means for said hydraulic motor including mechanism to vary the rate of hydraulic fluid delivery from said pump to said hydraulic motor.

6. In a mining machine, the combination with a main frame, of mining mechanism thereon, traction means for propelling said mining machine, mechanism for driving said traction means comprising a primary driving motor, a gear train interconnecting said motor and said traction means including a hydraulic pump driven by said primary driving motor, a hydraulic motor, drive gearing for connecting said hydraulic motor to said traction means, and control means for said hydraulic motor including mechanism to vary the rate of hydraulic fluid delivery from said pump to said hydraulic motor by controlling a by-pass for said pump.

7. In a mining machine, the combination with a main frame, of mining mechanism thereon, traction means for propelling said mining machine, mechanism for driving said traction means comprising a primary driving motor, a high speed drive comprising a disconnectable mechanical gear train interconnecting said motor and said traction means, a low speed drive comprising a disconnectable gear train interconnecting said motor and said traction means including a hydraulic pump driven by said primary driving mining mechanism by propelling the entire mining machine including a source of hydraulic fluid under pressure, a control valve, a hydraulic motor, and means for variably adjusting the feed rate of said mining mechanism to any one of a plurality of predetermined maintained speeds when said control valve is in its normal open position, said last named means including an adjustable member, there being a predetermined maintained speed for each position of adjustment of said adjustable member.

9. In a mining machine, the combination with a a supporting framework, of mining mechanism mounted thereon, means for driving said mining mechanism, hydraulic mechanism for feeding said mining mechanism by propelling the entire mining machine including a source of hydraulic fluid under pressure, a control valve, a hydraulic motor, and a volume control valve for variably adjusting the feed rate of said mining mechanism to any one of a plurality of predetermined maintained speeds when said control valve is in its normal open position said volume control valve including an adjustable member, there being a predetermined maintained speed for each position of adjustment of said adjustable member.

10. In a mining machine, the combination with a supporting framework, of a kerf cutter having an endless bit carrying cutter chain, a motor for driving said cutter chain, hydraulic mechanism for feeding said kerf cutter by propelling th entire mining machine including a source of hydraulic fluid under pressure, a control valve, a hydraulic motor, and means for variably adjusting the feed rate of said kerf cutter to any one of a plurality of predetermined maintained speeds when said control valve is in its normal open position there being a predetermined maintained speed for each position of adjustment of said adjustable member.

11. In a mining machine, the combination with a supporting framework, of a kerf cutter having an endless bit carrying cutter chain, a motor for driving said cutter chain, hydraulic mechanism for feeding said kerf cutterby propelling the entire mining machine including a source of hydraulic fluid under pressure, a control valve, a hydraulic motor, and a volume control valve for variably adjusting the feed rate of said kerf cutter to any one of a plurality of predetermined maintained speeds when said control valve is in its normal open position, said volume control valve including an adjustable member, there being a predetermined maintained speed for each position of adjustment of said adjustable member.

ROBERT K. JEFFREY. RICHARD D. NICHOLS.

Deceased. 

